Forming machine



April 6, 1948. r o. co 2,439,077

FORMING MACHINE Filed May 29, 1946 2 Sheets-Sheet 1 'INVENTOR Guy 0.Conner Fig.1.

April 6, 1948. e. o. CONNER FORMING MACHINE Filed May 29, 1946 2Sheets-Sheet 2 Guy 0. g c i er Patented Apr. 6, 1948 UNITED STATESPATENT OFFICE FORMING MACHINE Guy 0. Conner, Cleveland Heights, OhioApplication May 29, 1946, Serial No. 672,957

6 Claims. (Cl. 164-436) closest together move laterally generally in thesame direction. Such forming machines are disclosed, for example, in myPatent No. 2,406,808.

It has been customary, as, for example, in forming machines of the typedisclosed in my said patent, to gear directly together opposed shafts onwhich opposed forming heads are respectively mounted. This has beenentirely satisfactorywhen the distance between the axes of said shaftshas been relatively short. As the distance between the shafts increasesthe pitch diameter of gears carried by the shafts and which intermeshwith each other increases apace. But as the pitch diameter of the gearsincreases the peripheral velocity of the gears likewise increases inproportion for a given speed of operation of the machine in cycles perminute.

It may be desirable to space the respective shafts carrying the workingheads widely apart, as, for example, to provide unusually great diespace or to allow for the positioning of feeding or other means betweenthe shafts. If the distance between the shafts is increased above thatdistance which causes the peripheral velocity of opposed intermeshinggears for the desired speed of the machine in cycles per minute toexceed about 5200 feet per minute gear wear increases very rapidly. Itis important that the peripheral velocity of the gears be kept wellbelow the critical value.

I provide means for operating a forming machine having the shafts whichcarry the forming heads widely spaced but which does not require thegears to operate at a peripheral velocity undesirably close to thecritical, point even for the highest speeds at which the machine islikely to be operated. I do away with large directly intermeshing gearson the shafts which carry the working heads. Oh those shafts I providegears of materially smaller pitch diameter than the distance between theshaft axes. I provide supplementalgearing for causing operation of theopposed shafts so that they rotate in opposite directions but at thesame speed.

I provide a forming machine comprising op-.- posed parallel shafts,gears on said shafts, the pitch diameters of said gears being materiallyless than the distance between the axes of said shafts, other gearsmeshing with said first mentioned gears whereby said shafts rotate inopposite directions at the same speed, eccentric means on said shaftsand cooperating forming heads operable by said eccentric means so thatupon rotation of 'said shafts said heads partake of motion toward andaway from each other .and when closest together move also laterallygenerally in the same direction. I also preferably employ counterweightmeans counterbalancing the working heads. The counterweight means may bemounted on eccentrics on the shafts carrying the working heads but whicheccentrics are different from the eccentrics on which the working headsare mounted.

I preferably provide shaft means additional to the shafts which carrythe working heads disposed generally intermediate said shafts andparallel thereto and gears on said additional shaft means meshing withgears on the headcarrying shafts whereby the head-carrying shafts rotatein opposite directions at the same speed.

Other details, objects and advantages of the invention will becomeapparent as the following description of a present preferred embodimentthereof proceeds.

In the accompanying drawings I have shown a present preferred embodimentof the invention, in which Figure 1 is a vertical cross-sectional viewthrough a forming machine, the section being taken transversely of thedirection of feed of work through the machine, and

Figure 2 is a vertical cross-sectional view taken on the line II-II ofFigure l.

Referring now more particularly to the drawings, there is shown aforming machine having an upper forming head 2, a lower forming head 3,an upper counterweight 4 and a lower counterweight 5. The upper head 2and the upper counterweight 4 are mounted on two parallelupper shafts 6and I. The lower head 3 and the lower counterweight 5 are mounted on twoparallel lower shafts 8 and 9. All four of the shafts 8, I, 8 and 9 areparallel to one another, the shafts 6 and I lying in a horizontal planeand the shafts 8 and 9 lying in a lower horizontal plane. The shafts 6and 8 lie in the same vertical plane and the shafts I and 9 lie in thesame vertical plane.

The shafts 8 and I are rotated in one direction and the shafts 8 and 9are rotated in the opposite direction. Referring to Figure 2, if, forexample, the shafts 8 and I rotate clockwise the shafts 8 and 8 rotatecounterclockwise. The outer or right hand ends of the shafts viewingFigure l are mounted in outboard bearings l0. All four shafts arerotated in unison at the same speed by driving mechanism now to bedescribed.

The shafts 8, I, 8 and 9 carry respectively in plane A (Figure 1) gears45, 48, 41 and 48. These gears, as clearly appears in the drawings. havepitch diameters materially less than the distance between the axes ofopposed shafts, as, for example, shafts 6 and 8, The gears 45 and 46 aregeared together by a gear 49 keyed to a shaft 50. The gears 41 and 48are geared together by a gear keyed to a shaft 52. The shafts 58 and 52are parallel with the shafts 6, I, 8 and 9. The axis of the shaft 50 isdisposed in the plane defined by the axes of the shafts 6 and I and isequidistant from said axes. The axis of the shaft 52 is disposed in theplane defined by the axes of the shafts 8 and 9 and is equidistant fromsaid axes. The gears 49 and 5| are disposed in plane A.

In plane B there is keyed to the shaft 1 a gear 53 identical with thegear 46 and there is keyed to the shaft 52 a gear 54 identical with thegear 5|. Mounted generally between the upper and lower sets of shaftsare two intermediate shafts 55 and 56. In plane B there is keyed to theshaft 55 a gear SI'Which meshes with the gears 53 and In plane c thereis keyed to the shaft 8 a gear 58 identical with the gear 41 and thereis keyed to the shaft 50 a gear 59 identical with the gear 49. In planeC there is keyed to the shaft 56 a gear 60 which meshes with the gears58 and 59.

As will be seen from the above explanation the opposed shafts 6 and 8and the opposed shafts 1 and 9 are not directly intergeared but insteadthe respective shafts 6 and I are indirectly geared to the respectiveshafts 8 and 9 so that all four of those shafts rotate simultaneously atthe same speed, the shafts 6 and I in one direction and the shafts 8 and9 in the opposite direction. The driving mechanism may be operated bydriving any one of the shafts 6, I, 8. and 9,'

a driving gear 6| being shown on the shaft 8 (Figure 1) adapted to beoperated from any suitable source of power. The gear 6| may be replacedby an equivalent driving element such,

for example, as a pulley or a sprocket.

Thus the forming machine is driven by gearing composed of gears'ofrelatively small pitch diameters which operate the shafts in preciselythe same manner as though opposed shafts were directly intergeared butwithout the employment oflarge gears which would operate at undesirablyhigh peripheral velocities.

Each of the shafts 6, I, 8 and 9 comprises portions I I and I2 forjournaling the shaft for rotation and, intermediate those portions,eccentric portions I3, I4 and Ma. The portion II is concentric with theshaft axis. The portion I2 is eccentric with respect to the shaft axisbut is adapted to receive thereover an eccentric sleeve I2a (Figure 1)keyed thereto. When the eccentric sleeve I2a is applied to the shaftportion I2 the outer cylindrical surface of the sleeve I2a is concentricwith the shaft axis. Therefore, the shaft rotates in bearingscooperating with the portion II of the shaft and the sleeve I2a keyed tothe shaft.

The eccentric shaft portions I3 and Ma form eccentrics for mounting oneof the heads, as, for example, the upper head 2. The head straddles thecounterweight which is mounted about the eccentric shaft portion I4. InFigure 1 the high points of the eccentrics I3 and [4a are disposedupwardly. The eccentric for mounting the counterweight is shown at I5,being keyed to the shaft and its high point extending downwardly ordiametrically opposite the high points of the eccentrics I3 and Ma. Theeccentric I5 is applied to the shaft at the eccentric portion I4 thereofas shown in Figure 1, being keyed thereto by a key I5a.

Each shaft has a radial flange I6 against which lies a member I! whichthrough projections Iii carried thereby and which respectively enterrecesses I9 in the flange I6 is held against turning movement relativelyto the shaft. The member H has a circumferential series of teeth 20facing axially toward the right viewing Figure 1.

An eccentric sleeve 2| having a radial flange 2 la is mounted on theeccentric I3 and has teeth 22 normally in mesh with the teeth 20. Thesleeve 2I in its normal position is disposed relatively to the eccentricI3 so that the high point of the sleeve'is in the same plane containingand in the same direction from the shaft axis as the high point of theeccentric. In its end face the flange 2Ia has radial projections 23which are radially aligned with each other and one of which passesthrough the high point of the eccentric sleeve. An annular member 24 isdisposed about the shaft to theright of the sleeve 2I viewing Figure 1and has in its left hand face viewing such figure aligned radial slots25 and in its right hand face other aligned radial slots which extend atright angles to the slots 25. The bore of the annular member 24 is, asshown, much larger than the shaft so that the member 24 is free to movetransversely of the shaft as well as angularly. The radial projections23 enter and are guidingly received by the slots 25 so that the sleeve2| and the-annular member 24 may not rotate relatively to one anotherbut may partake only of relative movement longitudinally of theprojections 23, this being permitted because the bore of the member 24is larger than the shaft.

Mounted-over the eccentric I5 is an eccentric sleeve 3i having alignedradial projections 3Ia at its left and right hand faces, all of whichprojections are in the same plane containing the shaft axis whichextends at right angles to a plane containing the shaft axis and passingthrough the high point of the eccentric sleeve 3|. In other words, theprojections 3Ic on the end faces of the eccentric sleeve 3| lie in aplane perpendicular to the plane of the paper viewing Figure 1.

The projections 3Ia at the left hand face of the eccentric sleeve 3| areguidingly received by the slots 3Ib in the right hand face of theannular member 24. Thus the annular member 24 and the sleeve 3I may notrelatively rotate but may partake of relative movement longitudinally ofthe interfitting projections 3Ia and slots 3Ib. The sleeve 3I isnormally disposed with its high point in the same plane containing andin the same direction from the shaft axis as the high point of theeccentric I5.

Mounted next the sleeve 3I is a member 34 similar to the member 24 andhaving aligned radial slots 3Ic in its left hand face which extend atright angles to the plane of the paper viewing Figure 1 and alignedradial slots 36 in its right hand face, the slots 36 extending in theplane of the paper viewing Figure 1 and hence being disposed at rightangles to the slots 3Ic sleeve 39 having a flange 39a having alignedradial portions 39b, the eccentric sleeve 39 being similar to theeccentric sleeve 2|. The projections 39b extend through the high pointof the sleeve 39. The high point of the sleeve is normally in the sameplane containing and in onto the shaft and bears against the right. hand1 end of the sleeve |2a to hold the members assembled.

When one ofthe eccentric sleeves 2| and 39 and the shaft are relativelyturned the mechanism just described results in correspondinglyrelatively turning the other of such sleeves and the shaft and also inrelatively turning the eccentric sleeve 3| and the shaft to maintainparallel planes through the shaft axis and through the high points ofthe eccentric sleeves 2|, 39 and 3|. The result of this is to maintainthe high points of the resultant eccentrics or eccentric and eccentricsleeve combinations for the head and counterweight respectively directlyopposite each other relative to the shaft axis. This insures that thehead andcounterweight will always act on the shaft in oppositedirections. When the sleeve |2a is in place as shown in Figfrictionalresistance when turned up tightly against the sleeve flanges to hold thesleeves against turning. When the screws have been turned up to engagethe sleeve flanges and the outboard bearing in, nut 49b and sleeve l2ahave been removed a special sleeve is fitted over the end of the shaft,being keyed to the shaft so as to be non-rotatable with respect thereto.Turning of such sleeve turns the shaft so that it rotates relatively tothe sleeves 2|? and 39 which by the screws are fixedly held relativelyto the head so that they cannot turn. The connections above describedbetween the eccentric sleeves 2|, 3|- and 39 insure predeterminedrelative turning between the eccentric sleeve 3| and the shaft uponpredetermined relative turning between the eccentric sleeves 2| and 39and the shaft. As explained above, such connections insure that planesthrough the shaft axis and through the high points of the eccentricsleeves 2|, 3| and 39 are maintained parallel which in turn results inthe force of the counterweight always being exerted at a pointdiametrically opposite the point on the shaft at which the force of thehead is exerted.

When the shaft has been turned to the desired extent the special sleeveis removed, the screws 4| are threaded back clear of the sleeve flangesand the sleeve |2a, the nut 40b and the outboard ure 1 and the nut b isturned up against the end of that sleeve all of the eccentric sleeves2|, 3| and 39 are fixedly positioned relatively to each other andrelatively to the shaft just as though the sleeves ,were integral partsof the shaft. This is because the member I! is nonrotatably mounted onthe shaft, the teeth 20 on that member are in mesh with the teeth 22 onthe sleeve 2|, the sleeves 2| and 3| are held in fixed relation withrespect to each other by the annular member 24, the sleeves 3| and 39are held in fixed relation with respect to each other by the annularmember 34 and the teeth 40 on the sleeve 39 are in mesh with the teeth40a on the sleeve |2a, which sleeve |2a is keyed to the shaft. I

When it is desired to relatively angularly adjust the shafts and thesleeves carried thereby the outboard bearings III are removed, the nuts40!) are removed from the ends of the shafts and the sleeves |2a arelikewise removed. .This leaves the eccentric sleeves 2|, 3| and 39 looseupon their respective eccentrics |3, I4 and Ma and free to partake ofsufficient movement axially of the shafts to disengage the teeth 20 and22. Of course when the sleeve |2a is removed the teeth 40 and 40a aredisengaged. With all the teeth thus disengaged t e. sleeves 2|, 3| and39 are free to turn relati ely to the shafts.

To relatively angularly adjust the eccentric sleeves and shafts I holdcertain of the eccentric sleeves against rotation and turn the shaftstherein. I hold the eccentric sleeves 2| and 39 against movementrelatively to the head 2 by means of screws 4| which are mounted inthreaded bores in the head andare adapted to be turned so as to threadinwardly or toward the shaft until their noses engage the flanges 2|aand 39a of the sleeves 2| and 39, respectively. The screws 4| have fiatheads so that they create sufllcient bearing l0 arereplaced. The sleevesare then held in fixed position relatively to each other and to theshaft and the machine is again ready for operation.

Since the shafts are all geared together for op ration in unison it isonly necessary that ing nuts and sleeves. The holding sleevescorresponding to the sleeve |2a must be capable of movement toward theends of the shafts far enough to permit complete disengagement of bothsets of teeth corresponding to the teeth 29 and 22 and the teeth 40 and400. After the adjustment has been effected all of the screws 4| shouldbe turned back to clear the flanges of the eccentric sleeves and theholding sleeves and nuts should be applied to all four shafts. Theoutboard bearings shouldof course also be applied to all four shaftsbefore the machine is again put in operation.

The above described mechanism for adjust= ment of the relative angularpositions of the eccentric means and the shafts is claimed in mycopending application Serial No. 611,081.

While I have shown and described a present preferred embodiment of theinventioan it is to.

2. A forming machine comprising Opp sed parallel shafts, gears on saidshafts, the pitch diameters of said gears being materially less than thedistance between the axes of said shafts, other gears meshing with saidfirst mentioned gears whereby said shafts rotate in opposite directionsat the same speed, eccentric means on said shafts, cooperating formingheads operable by certain of said eccentric means so that upon rotationof said shafts said heads partake of motion toward and away from eachother and when closest together move also laterally generally in thesanie direction and counterweight means operable by other of saideccentric means counterbalancing said heads.

3. A forming machine comprising opposed sets of parallel shafts, shaftsof the respective sets being opposed to each other, gears on saidshafts, the pitch diameters of said gears being materially less than thedistance between the axes of opposed shafts, other gears meshing withsaid first mentioned gears whereby the shafts of one set rotate in thesame direction at the same speed and the shafts of the opposed setrotate in the same direction contrary to the direction of rotation ofthe shafts of the first mentioned set but at the same speed as that ofthe shafts of the first mentioned set, eccentric means on said shaftsand cooperating forming heads respectively operable by the eccentricmeans on the shafts of the respective sets so that'upon rotation of saidshafts said heads partake ofmotion toward and away from each other andwhen closest together move also laterally generally in the samedirection. v

4. A forming machine comprising opposed sets of parallel shafts, shaftsof the respective sets being opposed to each other, gears on saidshafts, the pitch diameters of said gears being materially less than thedistance betweenthe axes of opposed shafts, a pair of intermediateshafts parallel to said first mentioned shafts and disposed generallybetween the opposed sets, a gear on one of said intermediateshaftsmeshing with a gear on a shaft of one of said sets and also geared tothe shafts of the other of said sets, a gear on the other of saidintermediate shafts meshing with a gear on a shaft of the secondmentioned set and also geared to the shafts of the first mentioned set,whereby the shafts of the first mentioned set rotate in the samedirection at the same speed and the shafts of the second mentioned setrotate in the same direction contrary to the direction of rotation ofthe shafts of the first mentioned set but at the same speed as that ofthe shafts of the first mentioned set, eccentric means on the shafts ofsaid sets and cooperating forming heads respectively operable by theeccentric means on the shafts of the respective sets so that uponrotation of said shafts said heads partake of motion toward and awayfrom each other and when closest together move also laterally generallyin the same direction.

5. A forming machine comprising opposed sets of parallel shafts, shaftsof the respective sets being opposed to each other, gears on saidshafts, the pitch diameters of said gears being materially less than thedistance between the axes of opposed shafts, a pair of intermediateshafts parallel to said first mentioned shafts and disposed generally:between the opposed sets, a gear on one of said intermediate shaftsmeshing with a gear on a shaft of-one of said sets. and also geared tothe shafts of the other of said sets, a gear on the other of saidintermediate shafts meshing with a gear on a shaft of the secondmentioned set and also geared to the shafts of the first mentioned set,whereby the shafts of the first mentioned set rotate in the samedirection at the same speed and the shafts ,of the second mentioned setrotate in the same direction contrary to the direction of rotation ofthe shafts of the first mentioned set but at the same speed as that ofthe shafts of the first mentioned set, eccentric means on the shafts ofsaid sets, cooperating forming heads respectively operable by certain ofthe eccentric means on the shafts of the respective sets so that uponrotation of said shafts said heads partake of motion toward and awayfrom each other and when closest together move also laterally generallyin the same direction and counterweight means operable by other of saideccentric means counterbalancing said heads.

6. A forming machine comprising opposed sets of parallel shafts, eachset comprising three shafts, the respective shafts of the respectivesets being opposed to each other, gears on the outer two shafts of eachset, the pitch diameters of said gears being materially less than thedistance between the axes of the. opposed outershafts, a pair ofintermediate shafts parallel to the shafts of said sets and disposedgenerally between the opposed sets, a gear on one of said intermediateshafts meshing with a gear on an outer shaft of one of said sets andalso with a gear on the. center shaft of the other of said sets, a gearon the other of said intermediate shafts meshing with a gear on an outershaft of the second mentioned set and also with a gear on the centershaft of the first mentioned set,- whereby the outer shafts of the firstmentioned set rotate in the same direction at the same speed and theouter shafts of ,the'second mentioned set rotate in the same directioncontrary to the directionlof rotation of the outer shafts of the firstmentioned set but at the same speed as that of the outer shafts of thefirst mentioned set, eccentric means on the outer shafts of said setsand cooperating forming heads respectively operable by the eccentricmeans on the outer shafts of the respective sets so that upon rotationof said shafts said heads partake of motion toward and away from eachother and when closest together move also laterally generally in thesame direction.

GUY 0. CONNER.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Name Date 846,362 wift Mar. 5, 19071,973,515 Talbot Sept. 11, 1934 2,258,339 Sieger Oct. 7, 1941 FOREIGNPATENTS Number Country Date 510,848 Great Britain Aug. 9, 1939

